Rotary engine and pump



Nov. 1938. R. J. F. MOORE I ROTARY ENGINE AND PUMP Filed Sept. 14, 1935I/III 2 sheds-sheet 1 Nov. 8, 1938. R. J. F. MOORE ROTARY ENGINE ANDPUMP Filed Sept. 14, 1935 2 Sheets-Sheet 2 and to power transmissionmechanisms embodyrotary engines and/or pumps and by means of PatentedNov. 8, 1938 ROTARY ENGINE AND PUMP Raymond John Francis Moore,Oakleigh, Australia Application September 14, 1935, Serial No. 40,646

In Australia September 15, 1934 ll Claims.

This invention relates to improvements in and connected with rotarypumps, engines and the like, and refers especially to rotary pumps andengines adapted for use with liquids and gases,

ing such engines and pumps.

Power transmission mechanisms in accordance with the invention may beemployed for the propulsion of motor vehicles and for many otherpurposes.

One object of the present invention is to provide improvements in theconstruction and operation of rotary pumps and engines.

A further object is to provide simple and emcient power transmissionmechanisms embodying which forward and reverse movements at uniformlyvariable speeds, and freewheeling, clutch and braking effects may bereadily obtained.

One broad feature, of the invention resides in providing a rotary engineor pump having a cylin-' der, a rotor adapted to be disposedeccentrically within the cylinder, at least one blade member pivotallymounted on the rotor and adapted to make sealing contact with theperiphery of the cylinder, a rotor sealing face on each of the blademembers and disposed concentrically with the pivotal axis thereof, and acoacting sealing face on the rotor and disposed between said firstmentioned rotor sealing face and the pivotal axis of the blade, saidrotor sealing faces being arranged adjacent the free ends of therespective blade members.

More particularly, each of said blade members may comprise an armpivotally mounted on the rotor and a headpiece of substantially arcuateform at the outer end of said arm, said headpiece corresponding in widthto the rotor and having portion of its curved inner face hereinaftertermed the rotor-sealing face disposed concentric with the pivotal axisthereof and arranged in close proximity to the correspondingly curvedside of a slot provided in the rotor and adapted to accommodate aportion of or the inner end of the headpiece.

The outer end of the headpiece is adapted to make sealing engagementwith the periphery of the cylinder and for that purpose it may be formedwith a sealing face corresponding in ourvature to the cylinder andextending on both sides of an arc produced from said rotor-sealing faceon the inner surface of said headpiece.

This construction, when employed in an engine, permits of said rotorbeing driven in one direction only and likewise, when employed in apump,

liquid will be delivered thereby only when said rotor is rotated in theopposite direction.

Alternatively, two sets ,of oppositely extending pivoted blade membersmay be mounted alter nately on the rotor, and the cylinder-sealing faceat the outer end of each headpiece-4.. e. the face adapted to engage theperiphery of the cylindermay be disposed entirely inside or entirelyoutside an arc produced as aforesaid from the rotorsealing face on theinner surface of said headpiece.

When this construction is employed in an engine, the rotor is capable ofbeing driven in either direction by a fluid under pressure and likewise,when used in a pump, liquid may be delivered thereby irrespective of thedirection of rotation of said rotor.

A further important feature of the invention resides in the provision ofa rotary pump or engine having an open-ended cylinder, a rotor withinthe cylinder, members on the rotor adapted to make sealing contact withthe periphery of the cylinder, an outer casing enclosing the cylinder,means for displacing the cylinder relatively to the rotor to vary theeccentricity thereof whereby the displacement capacity of the saidengine or pump may be regulated and means whereby the cylinder issubjected externally to fluid pressures corresponding to the fluidpressures in the interior thereof.

More particularly the cylinder may be so arranged that its axis may bemoved through a rectilinear path extending through the axis of the rotorit being understood that, when the cylinder is concentric with therotor, no liquid will be delivered (in the case of a pump) even thoughthe rotor is being rotated, whilst, when the cylinder axis is disposedon one side of the rotor axis, the direction in which liquid isdelivered is opposite to the direction in which said liquid will bedelivered when the cylinder axis is on the opposite side of the rotoraxis, the direction of rotation of the rotor remaining unchanged.

Having set forth the object and nature of the invention, reference willbe made to the accompanying sheets of explanatory drawings wherein:-

Figure 1 is a view in sectional elevation of a rotary engine or pump inaccordance with the present invention.

Figure 2 is a view in sectional side elevation taken on the line 2-2 ofFigure 1; I

Figure 3 is a diagrammatic view similar to Figure 1 and illustrating theaction of the engine or taken on the line I'I of Figure-6.

Figure 8 is a detail view of portion of one of the blades shown inFigures 6 and 7 and is drawn to a larger scale. 7 V 1 Figure 9 is a viewsimilar to Figure 8 and shows a blade of modified construction.

Figure 10 is a view similar to Figure 6 and shows a reversible engine orpump having a non-displaceable cylinder; and

Figure 11 is aview similar to Figure l and shows a shock absorber inaccordance with the invention.

Referring to Figures 1 and 2 the reference numeral I designates acircular cylinder open at both ends and arranged within an annularholder The width of the cylinder I0 is equal to that of the annularholder and the inner diameter of the latter is substantially greaterthan the external diameter of said cylinder.

The cylinder is provided externally with a pair of diametrically opposedprojecting guides 12 of approximately rectangular form which are adaptedto be received in corresponding guide slots I3 formed transversely inthe inner periphery of the annular holder. These guide slots I3 are ofsuch depth as to permit of the cylinder being displaced in its own planewhereby the axis thereof may coincide with the axis of the annularholder or may be arranged on either side thereof.

Diametrically opposed ports I4 are provided in the periphery of thecylinder at right angles to the above-mentioned projecting guides I2 andcorresponding ports I5 provided in the annular holder are disposed inalignment therewith.-

The thickness of the cylinder wall is preferably increased somewhat inthe neighborhood of the ports I4 in order to provide increased strength,

and it will be noted that this increase in thickness does notnecessitate an increase in the internal diameter of the annular holderII in view of the fact that, when the cylinder is displaced within theholder, the ports in said cylinder are moved in a directionsubstantially parallel to the adjacent portions of the inner peripheryof said holder.

An end plate I6 corresponding in diameter to the outer diameter of theannular holder II is arranged at each end thereof. and a liquid-tightseal is formed therebetween by means of a plurality of clamping boltsI'I passing through the said discs and the intermediately disposedholder.

An outer casing I8 encircles the said end discs and the annular holder,and this casing is provided with a radial slot I9 having lugs 20 at eachside thereof to receive one or more clamping bolts 2| whereby the holdermay be contracted to close ly engage the outer peripheries of the saidend discs and annular holder and form a fluid tight joint therebetween.

This outer casing is also provided with bifurcated fluid passages 22 theinner ends of which are disposed in alignment with the said ports I4 andI5, in the cylinder and annular holder respectively.

A driving spindle 23 passes axially through-one of the end plates I6 andone end of said spindle is mounted in a closed bearing 24 in theopposite end plate.

In order to prevent the passage of liquid through the open bearing atthe right hand side of the pump (Figure 2) a grooved ring 24 ispreferably secured on the spindle within a recess provided in a boss onthe adjacent end plate I6, said recess being closed at its outer end bya fixed annular disc 25 which has a neat fit on the spindle.

Any liquid thrown outwards from the ring 24 is discharged from therecess through a passage 26 A rotor 21 is secured to the spindle withinthe cylinder I0 and the width of said rotor corresponds with the widthof the cylinder and of the annular holder II whereby the opposite endsof said rotor are disposed in close proximity to the inner faces of theend plates. Preferably the rotoris so mounted on the spindle as to becapable of a slight rocking movement whereby it will automatically alignitself with the said end plates. This rotor is disposed concentricallywith the annular holder II as will be clear from the drawings and fromthe preceding description, and the diameter of said rotor is less thanthe diameter of the cylinder.

A plurality of blade members 28 are'pivoted to the rotor and areregularly spaced thereon. These blades are adapted to make sealingcontact at or adjacent to their outer ends with the inner periphery ofthe cylinder I0 and the radial length of the blades is greater than thedifference between the diameter of the rotor and that of the cylinderwhereby a line drawn from the pivotal axis of a blade to the sealingsurface thereof will make an acute angle with the portion of thecylinder periphery which is engaged thereby.

Each of these blade members 28 may consist of a centrally disposed arm29 having an integral headpiece 30 of approximately arcuate shape at itsouter end (see Figure 4) .The inner end of each arm 29, the thickness ofwhich is substantially less than that of the rotor 21, is mounted on apivot pin 3i passing transversely between a spaced pair of lugs 32 onthe periphery of the rotor.

Alternately, each of the pivoted blades may be mounted as shown inFigure 5 wherein the rotor 21a is split as indicated at 28a and each lug32a is providedwith' an opening for receiving the stub shafts 3Ia. whichare formed integral with the inner end of the arm 29.-

The width of the headpiece 30 corresponds with that of the rotor wherebythe sides of said headpiece are disposed in sealing relationship withthe inner surfaces of the corresponding end plates I 5.

The rotor is formed with a plurality of transverse slots correspondingin number to the pivoted blades 28 and these slots are so arranged as toaccommodate the inner ends of the headpieces of said blades.

The inner portion 33 of the curved inner surface of each headpiece 30 isconcentric with the pivotal axis thereof and the corresponding side 34of the rotor slot therefor is similarly curved and is disposed in suchclose proximity thereto as to prevent liquid passing from the slot belowthe blade into the pocket or space therebehind, or vice versa.

This curved inner surface 33 of the headpiece 3B of the pivoted blade ishereinafter referred to as the rotor-sealing surface. The outer end ofthe headpiece 30 forms a sealing face 35 to closely engage the innerperiphery of the cylinder l0 and this sealing face, hereinafter calledthe cylinder sealing face, corresponds in curvature to the cylinder andis concentric therewith when said cylinder i0 is concentric with therotor 21.

Furthermore, this cylinder-sealing face 35 extends on both sides of anarc produced from the aforementioned rotor-sealing surface 33 on 'theheadpiece as shown in Figures 3 and 4.

Compression springs 36 may be arranged between the arms 29 of the blademembers 28 and the adjacent portions of the rotor in order that saidblades will remain in engagement with the cylinder surface even when thepump is not being actuated.

These springs 38 are preferablyarranged as shown to prevent theirfalling out in the event of breakage.

The cylinder l0 may be displaced in any approved manner as for exampleby means of a crank, pin 3'! engaging a transverse slot 38 in one faceof one of the projecting guides l2 on the outer surface thereof. Thiscrank pin is formed on the inner end of the spindle 39 projectingthrough a suitable sealing sleeve in the corresponding end plate l6 ofthe pump and an arm ll or other member is mounted on the outer endthereof to enable same to be actuated as desired.

It will be clear that, by rotating the crank pin 3? through an angle of180, the cylinder will be displaced whereby its axis moves from aposition at one side of the rotor axis to a corresponding position onthe opposite side thereof, and that, when the cylinder is disposed inits midposition, it is concentric with the rotor.

From the foregoing description it will be understood that the fluidpressures inside and outside the displaceable cylinder it) arepractically balanced, and consequently that the effort necessary to movethe cylinder is quite small. As a result, there is little tendency forthe leakage of fluid past the sides of the displaceable cylinder.

Furthermore, the diametrically opposed projecting guides IE on theexterior of the cylinder are each provided with suitable means to enablefluid from the spaces between the cylinder and the annular holder H topass to and from the ends of the guide slots l3 for said projections.For this purpose a slot 52 may be formed in one side of each of theguides I2.

When the device is used as a pump, the rotor is rotated in the directionof the arrows in Figures 1 and 3, while, when it is used as a motor, itis rotated in the opposite direction.

When the cylinder i0 is disposed concentrically with the rotor 27, noliquid will be delivered by the pump even though the rotor is beingactuated in the direction of said arrows, owing to the fact that, underthese conditions, the closed pockets formed by adjacent blade members 28do not vary in volume while passing around the cylinder. In other words,said blade members do not undergo angular'movement when the cylinder isconcentric with the rotor. 4

When, however, the cylinder is disposed eccentrically to the rotor asshown, the volumeof each of said pockets varies progressively duringrotation and liquid is accordingly drawn into the left-hand port I4 andis discharged through the port opposite thereto. When, on the otherhand,

the axis of the cylinder is disposed on the opposite side oi the axis ofthe spindle, the direction of flow of liquid is reversed though therotor continues to move in'the original direction. Also, the degree ofeccentricity determines the volume of liquid which is delivered duringeach complete revolution of the rotor. It will thus be seen that,although the rotor 21 revolves in one direction only, liquid may bepumped in either direction and at any velocity up to the maximumcapacity of the pump merely by regulating the position of thedisplaceable cylinder ID in relation to the rotor.

Each of said rotor blades 28 is maintained in sealing engagement withthe inner periphery of the cylinder ID by the pressure of the fluidmedium, this result being obtained as clearly shown in Figure 3 byreason of the variation in the point of contact between the cylindersealing surface 35 of each blade and the cylinder periphery during therotation of the rotor. I

' In this connection, it may be explained, when a blade is disposed in aposition adjacent to the greatest radial distance between the rotor andthe cylinder wall, the cylinder-sealing face of said blade bears againstthe cylinder at oradjacent to its forward end, i. e. the end remote fromthe pivotal axis thereof and beyond an arc produced from the rotorsealing face 33 of the blade.

On the other hand, when a blade is disposed at the opposite side of thecylinder to that abovementioned, the inner end of the sealing face 35engages the cylinder periphery, i. e. the end of the sealing faceadjacent to the said pivotal axis and within an are produced from saidrotor face 35.

If, now, the direction of rotation of the rotor is reversed, no liquidwill be pumped as the fluid pressure will cause the blades to moveinwards out of engagement with the periphery of the cylinder. Thisaction will be clear from an inspection of Figure 3.

Alternatively, if the device is used as an engine and the cylinder I0 isdisposed as shownin Figures 1 and 3, fluid under pressure is deliveredto the right-hand passages 22 and the rotor is actuated in the oppositedirection to the arrows in Figures 1 and 3. If the cylinder i0 is movedwhereby its axis lies on the opposite side of the spindle axis, thefluid under pressure is supplied to the left-hand passages 22 and therotor moves in the same direction as before, i. e. in a directionopposite to that of the arrows in Figures 1 and 3.

If the device is to be used as a fluid clutch, the upper inlet anddischarge ports 22 may be connected by a passage 32 shown in brokenlines at the top of Figure 1, the passage being provided with a valve 63to control the flow of liquid therethrough and lower ports 22 areclosed. It will be clear hereafter that the construction shown inFigures 6 and 7 may be similarly used as a fluid clutch.

Assume now that the rotor is connected to a driving spindle whichrotates in the direction of the arrow and that the casing I8 isconnected to-a driven spindle. When the valve 43 is fully open, nomotion will be imparted to the .driven spindle as the liquid will bemerely circulated through the by-pass and the pump. When, on the otherhand, the valve 43 is closed, no liquid can pass through the by-pass andthe driven spindle will be rotated at the same speed as the drivingspindle. If, further, the valve is arranged at an intermediate position,the driven member will be rotated but at a lower speed than the drivingspindle depending on the slip occasioned by the flow of liquid throughthe by-pass.

As no liquid is pumped when the direction of movement of the rotor isreversed, it will be clear that a ratchet effect may be obtained byoscillating the rotor.

In the modification of the invention shown in Figures 6 and 7, asomewhat modified form of blade 23 is employed and two direct coupledpumps are provided to minimize pulsations in the delivery of liquid andto more accurately balance the pressures on the cylinder, these pumpsbeing connected to common inlet and discharge passages.

For this purpose a partition plate I! is arranged between a pair ofdisplaceable cylinders ill constructed and arranged in the manner aboveset forth.

The two cylinders it, together with the partition plate 45, areconnected by dowell pins 44 and are mounted within an annular holder IIwhich is fitted with end plates l and arranged within a contractibleouter casing 13 substantially in the manner above set forth.

The rotors 21 in the cylinders III are so disposed on the spindle 23that there is a phase displacement between the pivoted blades 23 of thedifferent pumps, e. g. in the case of the two pumps shown the blades inone pump are disposed one half of the blade pitch in advance of theblades in the other pump.

If desired, more than two pumps may be arranged in this way.

On referring to Figure 7 it will be noted that the rotor and associatedparts have been omitted from the left-hand cylinder in order to showthat the ports ii are disposed obliquely whereby uniform wear of theblade surfaces will be ob-,

tained.

Each rotor 21 is provided with two sets of oppositely extending pivotedblades 28 which are arranged alternately whereby each adjacent pairthereof constitutes a unit.

The blades are formed with arms and with substantially arcuateheadpieces in the manner previously described and the inner ends of eachadjacent pair of headpieces are adapted to be received into a commonslot formed transversely in the outer surface of the rotor.

Each side of each of said slots is curved vto conform to the pivotalaxis of the corresponding blade or headpiece and the adjacent innersurface of said arcuate headpiece is disposed in close proximity theretoto prevent the passage of liquid below the headpiece into the space orpocket therebehind as in the case of the pump previously described.

These pivoted blades 28 are similar to the blades shown in Figures .1 to4 except that the cylinder sealing surface 35 at the outer end of theheadpiece 30 thereof is disposed completely inside an are produced fromthe rotor sealing surface on the curved inner face of said headpiece(see also Figure 8).

In other words, the distance between the cylinder sealing surface 35 andthe pivotal axis of the blade is less than the radius of the rotorsealing surface 33.

With this construction it is desirable to provide means to relieve thepressure within the transverse slots 34 in the rotor when said slots aresuccessively disposed at the minimum distance from the cylinder surfaceand for this purpose a diametrically opposed pair of ports 33 isprovided in the inner surface of each of the end plates.

A pair of passages 41 connect each' of these ports 43 with ports 43 alsoprovided in the inner faces of the end plates l3 and so disposed as tobe covered by the respective cylinder ll when the latter is in itscentral, i. e. its concentric position.

When, however, said cylinder is moved in either direction from itscentral position, the ports at the outer end of the correspondingpassages are uncovered to permit of the escape of liquid from the rotorslots successively registering with the port 43 at the inner end thereof(see lower portion of Figure 6). I

Each of the passages 41 is provided with a nonreturn valve 4| to preventthe passage of liquid into the rotor slots 32 and it will thus be clearthat any liquid discharged from a rotor slot into a port 43 passesoutwardly through that one of the corresponding passages 41 whichcommunicates with the induction side of the pump. Although, for thepurposes of illustration, these passages 41 are shown as extendingthrough projections on the end plates I6, they are preferably providedin the end plates themselves.

When this arrangement is used as a pump, the rotor may be moved ineither direction and the direction of flow of the liquid for a givendirection of rotation is determined solely by the position of thedisplaceable cylinders II in relation to the axis of the spindle.

Likewise, the device may be used as a motor by supplying fluid underpressure to either side of the cylinders, the direction .of rotation ofthe rotor being then determined by whether the cylinder axis is above orbelow the axis of the spindle.

It is important to note that this result is due to the use of opposedpairs of pivoted blades 23 having their cylinder sealing surfacesdisposed entirely on one side of an are produced from the correspondingrotor sealing faces.

By way of illustration, let it be assumed that the device is being usedas a pump and that the rotor is turned clockwise in Figure 6. It willthen be clear that the trailing blades are effective at the upper arcsof the cylinders in that figure while the opposite blades of each pair(viz those having their headpieces in advance of. their pivots) areeffective at the lower arcs of the cylinders. In other words, one bladeof each opposed pair will be maintained in contact with the cylinderwall by the fluid pressure aided by the spring 30.

In lieu of employing pivoted blades 23 having their cylinder sealingsurfaces 36 disposed within an arc produced from the rotor sealingsurface 33, said faces 35 may be disposed outside said arc as shown inFigure 9.

Figure 7 also illustrates a preferred manner of preventing leakage of.fluid through the bearing ,of the spindle 23.

For this purpose a sleeve 5i formed integrally with the resilient metaldisc 52 is clamped to the spindle 23 and the outer peripheral edge ofsaid disc is turned outwards and arranged to bear against the innersurface of an annular cover plate 53 which is secured in a fluid-tightmanner to the adjacent end plate ii of the pump.

It will be clear that any liquid under pressure which passes through thebearing of the spindle into the chamber enclosing the resilient discwill cause the latter to be firmly pressed against the annular coverand-so prevent the escape of the liquid except through an opening 26provided for the purpose.

It is not always necessary or desirable to use displaceable cylinders asshown in the figures previously described. For example, when theinvention is used for the transmission gear of a motor vehicle, a pumpas shown in Figures 6 and 7 may have it rotor spindle connected to thepower shaft of the engine and a rotary motor of the same general typemay be rigidly connected to one or more road wheels.

By providing a displaceable cylinder in the pump, the speed ratio may bevaried from a predetermined value in one direction to the same value inthe opposite direction, and it is not necessary to provide displaceablecylinders in the rotary motors.

Referring now to Figure 10, the inner surface of each of thenon-displaceablecylinders iii, instead of being circular, preferablycomprises a segment d8 of relatively small radius disposed concentricwith the rotor axis, a concentric segment d9 disposed opposite to saidfirst mentioned segment and of increased radius, and an opposed pair ofeccentric curved surfaces 50 connecting the adjacent ends of thesegments 68 and d9 by means of smooth curves.

Inlet and discharge ports M are provided in said eccentric segmentalsurfaces 56 of the cylinder and correspond in width thereto. It willaccordingly be understood that pivoted blades 28 fitted to the rotor donot undergo angular movement when passing between the ports, as suchmovement takes place only when said blades are passing across the ports.

By means of this construction, wear and friction are reduced to aminimum because angular movement of the blades can take place only whenthe fluid pressures on opposite sides thereof are balanced.

Although, in order to illustrate the invention, the pumps and engineshave been described herein as forming part of the power transmissionmechanism, it will be clear that such engines and pumps may be employedfor any purpose and that same are adapted to'operation both with liquidsand gases.

In the case of a shock absorber (see Figure 11), I may arrange the rotorto make sealing contact at one point with the internal periphery of thecylinder, said rotor being fitted with a single pivoted blade member 28of the type shown in Figure 1, Figure 8 or Figure 9. A by-pass 55 isprovided in the cylinder and is fitted with an adjustable valve 56.

In use, the rotor may move freely in one direction, owing to the blademember 28 being pressed inwards towards the rotor while its return movement will be retarded to an extent depending on the valve opening in theby-pass.

I claim: 7

l. A rotary engine or pump having a substantially cylindrical chamber,the inner peripheral surface of which constitutes a smooth continuouscurve, said cylindrical chamber havingspaced inlet and discharge portscommunicating therewith, a rotor arranged eccentrically within thechamber and having its entire peripheral surface disposed out of sealingcontact with the inner periphery of said cylindrical chamber, aplurality of transversely arranged blade members pivotally supported onthe rotor adjacent its periphery, a headpiece at the free end of eachblade member, each said headpiece extending approximately radially ofthe rotor and being receivable in a coacting pocket in the peripherythereof, the inner face of each headpiece, with respect to the pivotalaxis thereof, being disposed in constant sealing relationship with acoacting face on the rotor, said coactlng face forming one side of thepocket for said headpiece, the entire outer face of each headpiece withrespect to the pivotal axis thereof being disposed out of sealingrelationship with the rotor at all times, the outer end of eachheadpiece, with respect to the rotor axis, being disposed in constantsealing engagement with the curved wall of the chamber, at least oneblade member being disposed at all times in contact with the cylinder ateach side of a line connecting the said inlet and discharge ports.

2. A rotary engine or pump having a substantially cylindrical chamber,the inner peripheral surface of which constitutes a smooth continuouscurve, said cylindrical chamber having spaced inlet and discharge portscommunicating therewith, a rotor arranged eccentrically within thechamber, a plurality of blade members pivotally supported on the rotoradjacent its periphery, a'headpiece at the free end of each blade memberand extending substantially radially of the rotor, transverse sealingfaces on the rotor, the inner face of each headpiece with respect to thepivotal axis thereof being disposed in constant sealing relationshipwith one of said transverse sealing faces on the rotor and the entireouter face of each headpiece, with respect to said pivotal axis thereof,being out of sealing relationship with the rotor at all times, the outerend of each headpiece with respect to the rotor axis, providing asurface for maintaining constant sealing engagement with the innerperiphery of the cylindrical chamber, characterized in that an arcstruck from the pivotal axis of the headpiece and produced from thecorresponding transverse sealing face on the rotor passes through saidsealing surface at the outer end of the headpiece, at least one blademember being disposed at all times in contact with the cylinder at eachside of a line connecting the said inlet and discharge ports.

3. A rotary engine or'pump having a substantially cylindrical chamberthe inner peripheral surface of which constitutes a smooth continuouscurve, said cylindrical chamber having spaced inlet and discharge portscommunicating therewith, a rotor arranged eccentrically within thechamber and having its entire peripheral surface disposed out of sealingrelationship with the inner periphery of the cylindrical chamber, aplurality of similarly arranged blade members pivotally supported on therotor adjacent its periphcry, a headpiece at the free end of each blademember, each headpiece extending approximately radially of the rotor andbeing receivable in a corresponding peripheral pocket in the rotor, theinner face of each headpiece with respect to the pivotal axis thereofbeing disposed in constant sealing relationship with a co'acting sealingface on the rotor, said coacting sealing face forming a portion of theboundary of the corresponding peripheral pocket in the rotor, the entireouter face of each headpiece with respect to the pivotal axis thereofbeing disposed out of sealing relationship with the rotor at all timesand the outer end of each headpiece, with respect to the rotor axis,having a cylinder sealing face to maintain sealing engagement with theperipheral surface of the cylindrical chamber, said cylinder sealingface extending on opposite sides of an arc struck from the pivotal axisof the headpiece and produced from the rotor sealing surface provided bysaid inner face of the headpiece, at least one blade member beingdisposed at all times in contact with the cylinder at each side of aline connecting the 'said inlet and discharge ports.

4. A rotary engine or pump according to claim 3 inlet and dischargeports communicating therewith, a rotor arranged eccentrically within thechamber and having its peripheral surface disposed entirely out ofsealing relationship with the peripheral surface of the chamber, aplurality of blade members pivotally supported on the rotor adjacent itsperiphery, said blade members being arranged in oppositely inclinedpairs, a headpiece at the free end of each blade member and extendingapproximately radially of the rotor, a plurality of transverse sealingfaces on the rotor, the inner face of each headpiece, with respect tothe pivotal axis thereof, being disposed in constant sealing engagementwith the corresponding transverse sealing face on the rotor, the entireouter face of each headpiece, with respect to the pivotal axis thereofbeing disposed out of sealing relationship with the rotor at all times,the outer end of each headpiece, with respect to the rotor axis, forminga cylinder sealing surface which is maintained in constant engagementwith the inner periphery of the cylindricalchamber characterized in thatsaid cylinder sealing surface is disposed at one side of an arc struckfrom the pivotal axis of the headpiece and produced from the rotorsealing surface at said inner face thereof, at least one blade memberbeing disposed at all times in contact with the cylinder at each side ofa line connecting the said inlet and discharge ports.

6. A rotary engine or pump having a substantially cylindrical chamber,the inner peripheral surface of which constitutes a smooth continuouscurve, said cylindrical chamber having inlet and discharge portscommunicating therewith, a rotor arranged eccentrically within thechamber and having its peripheral surface disposed entirely out ofsealing relationship with the peripheral surface of the chamber, aplurality of blade members pivotally supported on the rotor adjacent itsperiphery, said blade members being arranged in oppositely inclinedpairs, a headpiece at the free end of each blade member and extendingapproximately radially of the rotor, a plurality of transverse sealing.faces on the rotor,

the inner face of each headpiece, with respect to the pivotal axisthereof being disposed in constant sealing engagement withthecorresponding transverse sealing face on the rotor, the entire outerface of each headpiece, with respect to the pivotal axis thereof, beingdisposed out of sealing relationship with the rotor at all times, theouter end of each headpiece, with respect to the rotor axis, forming acylinder sealing surface which is maintained in constant engagement withthe inner periphery of the cylindrical chamber, characterized in thatsaid cylinder sealing surface is inside an arc struck from the pivotalaxis of the headpiece and produced from the rotor sealing surface atsaid inner face thereof, at least one blade member being disposed at alltimes in contact with the cylinder at each side of a line connecting thesaid inlet and discharge ports.

7. A rotary engine or pump having a'substantially cylindrical chamberthe inner peripheral surface of which constitutes a smooth continuouscurve, said cylindrical chamber having spaced inlet and discharge portscommunicating therewith, a rotor arranged eccentrically within thechamber and having its peripheral surface disposed entirely out ofsealing relationship with the periphof each headpiece, with respect tothe pivotal axis thereof, being disposed out of sealing relationshipwith the rotor at all times, the outer end of each headpiece, withrespect to the rotor axis, forming a cylinder sealing surface which ismaintained in constant engagement with the inner periphery of thecylindrical chamber, characterized in that said cylinder sealing surfaceis outside an arc struck from the pivotal axis of the headpiece andproduced from the rotor sealing surface at said inner face thereof, atleast one blade member being disposed at all times in contact with thecylinder at each side of a line connecting the said inlet and dischargeports.

8. A rotary engine or pump having a cylinder, the inner peripheralsurface of which constitutes a smooth continuous curve, said cylinderhaving spaced inlet and discharge ports communicating therewith, endmembers for the cylinder, a rotor mounted eccentrically within thecylinder and having its ends arranged in sealing relationship with saidend members for the cylinder, a plurality of blade members pivotallymounted on the rotor, a headpiece at the outer end of each of said blademembers, each headpiece having its sides arranged in sealingrelationship with said end members for the cylinder, a sealing surfaceon each of said headpieces in constant sealing engagement with theperiphery of the cylinder, the

inner face of each of said headpieces with respect to the pivotal axisthereof, being concentric with said pivotal axis and constituting aconcave sealing surface, and sealing surfaces on the rotor arranged tocoact with said concave sealing surface, the entire outer faces of saidheadpieces with respect to the pivotal axes thereof, being disposed outof sealing contact with said rotor at all times, at least one blademember being disposed at all times in contact with the cylinder at eachside of the centerline connecting the inlet and discharge ports, and thecylinder sealing surface on the headpiece of each blade member extendingon opposite sides of an are produced from the concave sealing surface ofsaid headpiece.

9. A rotary engine or pump having a cylinder, the inner peripheralsurface of which constitutes a. smooth continuous curve, said cylinderhaving spaced inlet and discharge ports communicating therewith, endmembers for the cylinder, a rotor mounted eccentrically within thecylinder and having its ends arranged in sealing relationship with saidend members for the cylinder, a plurality of blade members pivotallymounted on the rotor, a headpiece at the outer end of each of said blademembers, each headpiece having its sides arranged in sealingrelationship with said end members for the cylinder, a sealing surfaceon each of said headpieces in constant sealing engagement with theperiphery of the cylinder, the inner face of each of said headpieceswith respect to the pivotal axis thereof, being concentric with saidpivotal axis and constituting a concave sealing surface, and sealingsurfaces on the rotor an'anged to coact with said concave sealingsurface, the entire outer faces of said headpieces with respect to thepivotal axes thereof, being disposed out of sealing contact with saidrotor at all times, at least one blade member being disposed at alltimes in contact with the cylinder at each side of the centerlineconnecting the inlet and discharge ports, and the cylinder sealingsurface on the headpiece of each blade member lying inside an arcproduced from the concave sealing surface on said headpiece.

10. A rotary engine or pump having a cylinder, the inner peripheralsurface of which constitutes a smooth continuous curve, said cylinderhaving spaced inlet and discharge ports communicating therewith, endmembers for the cylinder, a rotor mounted eccentrically within thecylinder and having its ends arranged in sealing relationship with saidend members for the cylinder, .a plurality of blade members pivotallymounted on the rotor, a headpiece at the outer end of each of said blademembers, each headpiece having its sides arranged in sealingrelationship with said end members for the cylinder, a sealing surfaceon each of said headpieces in constant sealing engagement with theperiphery of the cylinder, the inner face of each of said headpieceswith respect to the pivotal axis thereof, being concentric with saidpivotal axis and constituting a concave sealing surface, and sealingsurfaces on the rotor arranged to coact with said concave sealingsurface, the entire outer faces of said headpieces with respect to thepivotal axes thereof, being disposed out of sealing contact with saidrotor at all times,'at least one blade member being disposed at alltimes in contact with the cylinder at each side of the centerlineconnecting the inlet and discharge ports, and the blade members beingarranged in oppositely directed pairs and the cylinder sealing faces onthe headpieces thereof being disposed inside arcs produced from theconcave sealing surface on said blade members.

11. A rotary engine or pump having a cylinder, the inner peripheralsurface of which constitutes a smooth continuous curve, said cylinderhaving spaced inlet and discharge ports communicating therewith, endmembers for the cylinder, a rotor mounted eccentrically within thecylinder and having its ends arranged in sealing relationship with saidend members for the cylinder, a plurality of blade members pivotallymounted on the rotor, a headpiece at the outer end of each of said blademembers, each headpiece having its sides arranged in sealingrelationship with said end members for the cylinder, a sealing surfaceon each of said headpieces in constant sealing engagement with theperiphery of the cylinder, the inner face of each of said headpieceswith respect to the pivotal axis thereof, being concentrio with saidpivotal axis and constituting a concave sealing surface, and sealingsurfaces on the rotor arranged to coact with said concave sealingsurface, the entire outer faces of said headpieces with respect to thepivotal axes thereof, being disposed out of sealing contact with saidrotor at-all times, at least one blade member being disposed at alltimes in contact with the cylinder at each side of the centerlineconnecting the inlet and discharge ports, the blade members beingarranged in oppositely directed pairs and said cylinder sealing surfacesdisposed at one side of an arc produced from the respective rotorsealing faces thereof, an outer casing, means for displacing thecylinder in its own plane within said casing, one of said membersclosing the end of the cylinder having a port therein, a passageconnecting said port with a further port in said end member, saidfurther port being closed by the cylinder wall when said cylinder is inthe neutral position and being opened to the space surrounding saidcylinder when the latter is displaced, whereby its axis is on theopposite side of the axis of the spindle from said ports, said firstmentioned port being arranged to successively register with the spacesbetween adjacent blade members when said spaces are disposed on theopposite side of the spindle axis to the axis of the cylinder.

RAYMOND JOHN FRANCIS MOORE.

